JPH0968197A - Impeller for centrifugal pump or compressor - Google Patents
Impeller for centrifugal pump or compressorInfo
- Publication number
- JPH0968197A JPH0968197A JP24254095A JP24254095A JPH0968197A JP H0968197 A JPH0968197 A JP H0968197A JP 24254095 A JP24254095 A JP 24254095A JP 24254095 A JP24254095 A JP 24254095A JP H0968197 A JPH0968197 A JP H0968197A
- Authority
- JP
- Japan
- Prior art keywords
- flow
- outlet
- blade
- inlet
- impeller
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Withdrawn
Links
- 239000012530 fluid Substances 0.000 claims abstract description 18
- 238000000926 separation method Methods 0.000 abstract description 4
- 238000010586 diagram Methods 0.000 description 2
- 238000011056 performance test Methods 0.000 description 2
- 238000005336 cracking Methods 0.000 description 1
- 230000012447 hatching Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は遠心式ポンプ又は圧
縮機の羽根車に関する。TECHNICAL FIELD The present invention relates to an impeller of a centrifugal pump or compressor.
【０００２】[0002]
【従来の技術】従来の遠心ポンプの羽根車が図３に示さ
れている。図３において、10は羽根車で、主板１と側板
２とこれらの間に架橋された複数（図には３個）の羽根
３によって限界された複数（図には３個）の羽根間流路
４を具えている。2. Description of the Related Art An impeller of a conventional centrifugal pump is shown in FIG. In FIG. 3, 10 is an impeller, which is a plurality (three in the figure) of inter-blade flow limited by a plurality of (three in the figure) blades 3 bridged between the main plate 1 and the side plate 2. It is equipped with road 4.
【０００３】しかして、ハブ５を図示しない回転軸に固
定して矢印方向に回転させると、流体は入口７から羽根
間流路４に流入し、羽根間流路４を流過する過程で付勢
されることにより昇圧して出口８から流出する。However, when the hub 5 is fixed to a rotating shaft (not shown) and rotated in the direction of the arrow, the fluid flows from the inlet 7 into the inter-blade passage 4 and is attached in the process of passing through the inter-blade passage 4. By being urged, the pressure is increased and the gas exits from the outlet 8.
【０００４】上記各羽根間流路４はその流路面積が入口
７から出口８にかけて滑らかに拡大するように決定さ
れ、入口７の相対速度Ｗ1 と出口８の相対速度Ｗ2 との
比Ｓは式１で示され、この比Ｓは１以下で、通常0.5 程
度に設定されている。[0004] each blade between passage 4 is determined such that the flow area is smoothly expanded from the inlet 7 toward the outlet 8, the ratio S between the relative velocity W 2 of the relative velocity W 1 and the outlet 8 of the inlet 7 Is expressed by Equation 1, and the ratio S is 1 or less, and is usually set to about 0.5.
【０００５】[0005]
【式１】 (Equation 1)
【０００６】[0006]
【発明が解決しようとする課題】上記従来の羽根車にお
いては、羽根間流路４内の流れが減速流れとなるため、
その流量揚程曲線は図４に示すように最高揚程点イより
低流量側で左下りとなる。In the above-mentioned conventional impeller, the flow in the inter-blade flow path 4 becomes a deceleration flow.
As shown in FIG. 4, the flow head curve is left-downward on the low flow side from the highest head point a.
【０００７】この結果、ポンプが低流量域で運転される
ときには、羽根３の後面3b側で流れが剥離したり、二次
流れが発生し、この影響により大きな非定常流体力が発
生して羽根車10の割れや配管系統の振動を引き起こすと
いう問題があった。As a result, when the pump is operated in the low flow rate region, the flow is separated on the rear surface 3b side of the blade 3 or a secondary flow is generated, and due to this influence, a large unsteady fluid force is generated and the blade is There was a problem that it caused cracking of the car 10 and vibration of the piping system.
【０００８】[0008]
【課題を解決するための手段】本発明は上記課題を解決
するために発明されたものであって、その要旨とすると
ころは、主板と側板とこれらの間に架橋された複数の羽
根によって複数の羽根間流路を限界してなる遠心ポンプ
又は圧縮機の羽根車において、上記羽根間流路の入口か
ら出口にかけて流過する流体の相対速度がほぼ一定にな
るように上記羽根間流路の流路面積を形成したことを特
徴とする遠心式ポンプ又は圧縮機の羽根車にある。The present invention has been invented to solve the above-mentioned problems, and its gist is to provide a plurality of main plates, side plates, and a plurality of blades bridged therebetween. In an impeller of a centrifugal pump or a compressor that limits the inter-blade flow path of the inter-blade flow path of the inter-blade flow path from the inlet to the outlet of the inter-blade flow path, the relative speed of the fluid is almost constant. The impeller of a centrifugal pump or compressor is characterized in that a flow passage area is formed.
【０００９】他の特徴とするところは、上記羽根の厚さ
を上記羽根間流路の入口から出口にかけて次第に厚くし
たことにある。Another feature is that the thickness of the blade is gradually increased from the inlet to the outlet of the inter-blade passage.
【００１０】しかして、羽根間流路を流過する流体の相
対速度は入口から出口にかけてほぼ一定となり、従っ
て、運転点が低流量域に入っても羽根間流路を流過する
流体の流速は減速しないので、羽根間流路内で流れが剥
離したり、二次流れが発生することはない。However, the relative velocity of the fluid flowing through the inter-blade passage is almost constant from the inlet to the outlet, so that the flow velocity of the fluid passing through the inter-blade passage even when the operating point enters the low flow rate region. Does not decelerate, so there is no separation of flow or generation of secondary flow in the inter-blade flow path.
【００１１】[0011]
【発明の実施の形態】本発明の１実施形態が図１に示さ
れている。図１に示すように、各羽根３の厚さを図にハ
ッチングで示すように羽根間流路４の入口７から出口８
にかけて次第に厚くすることによって羽根間流路４内を
流過する流体の相対速度が入口７から出口８にかけて一
定となるように羽根間流路４の流路面積が設定されてい
る。DETAILED DESCRIPTION OF THE INVENTION One embodiment of the present invention is shown in FIG. As shown in FIG. 1, the thickness of each blade 3 is indicated by hatching in the drawing, and the inlet 7 to the outlet 8 of the inter-blade flow path 4 are shown.
The flow passage area of the inter-blade flow passage 4 is set so that the relative velocity of the fluid flowing in the inter-blade flow passage 4 becomes constant from the inlet 7 to the outlet 8 by gradually increasing the thickness over time.
【００１２】従って、入口７の相対速度Ｗ1 と出口８の
相対速度Ｗ2 との比Ｓは式２で示され、この比Ｓはほぼ
１となる。なお、６は羽根３内に形成された腔所であ
る。Accordingly, the ratio S between the relative velocity W 2 of the relative velocity W 1 and the outlet 8 of the inlet 7 is shown in equation 2, the ratio S is approximately 1. In addition, 6 is a cavity formed in the blade 3.
【００１３】[0013]
【式２】 (Equation 2)
【００１４】他の構成は図３に示す従来のものと同様で
あり、対応する部材には同じ符号を付してその説明を省
略する。The other structure is the same as that of the conventional one shown in FIG. 3, and the corresponding members are designated by the same reference numerals and the description thereof is omitted.
【００１５】しかして、羽根間流路４を流過する流体の
相対速度は入口７から出口８にかけてほぼ一定となり、
従って、運転点が低流量域に入っても羽根間流路４を流
過する流体の流速は減速しないので、羽根間流路４内で
流れが剥離したり、二次流れが発生することはない。Therefore, the relative velocity of the fluid flowing through the inter-blade passage 4 becomes almost constant from the inlet 7 to the outlet 8,
Therefore, even if the operating point enters the low flow rate region, the flow velocity of the fluid flowing through the inter-blade flow path 4 is not reduced, so that the flow is separated in the inter-blade flow path 4 or a secondary flow is not generated. Absent.
【００１６】また、出口８における流れのすべり、即
ち、羽根３の前面3aと後面3bとの間に存在する圧力差に
より流体が出口８から流出するとき、前面3aから後面3b
に向かって押し流される割合も従来のものより小さくな
る。When the fluid flows out from the outlet 8 due to the slip of the flow at the outlet 8, that is, the pressure difference existing between the front surface 3a and the rear surface 3b of the blade 3, the front surface 3a to the rear surface 3b.
The rate of being swept away toward is also smaller than the conventional one.
【００１７】かくして、本発明の羽根車の性能試験結果
は図２にＯ印で示すようになり、その流量揚程曲線は低
流量域においても右下がり特性となる。なお、比較のた
め従来の羽根車のそれは図２に黒塗三角で示されてい
る。Thus, the result of the performance test of the impeller of the present invention is shown by the O mark in FIG. 2, and the flow head curve has a downward sloping characteristic even in the low flow area. For comparison, that of the conventional impeller is shown by a black triangle in FIG.
【００１８】[0018]
【発明の効果】本発明においては、羽根間流路の入口か
ら出口にかけて流過する流体の相対速度がほぼ一定にな
るように羽根間流路の流路面積を形成したため、羽根間
流路を流過する流体の相対速度は入口から出口にかけて
ほぼ一定となり、従って、運転点が低流量域に入っても
羽根間流路を流過する流体の流速は減速しないので、羽
根間流路内で流れが剥離したり、二次流れが発生するこ
とはない。According to the present invention, since the flow passage area of the inter-blade flow passage is formed so that the relative velocity of the fluid flowing from the inlet to the outlet of the inter-blade flow passage is substantially constant, the inter-blade flow passage is formed. The relative velocity of the fluid flowing through is almost constant from the inlet to the outlet, so even if the operating point enters the low flow rate region, the flow velocity of the fluid flowing through the inter-blade flow passage does not slow down, so in the inter-blade flow passage. There is no separation of flow or secondary flow.
【００１９】また、出口における流れのすべりを従来の
ものに比し低減できる。そして、流量揚程曲線は低流量
域においても右下がりとなるので、キャビテーション等
により圧力変動が発生してもこれにより流量が容易に変
動することはないので、運転が安定し、騒音や振動を抑
制できる。Further, the slip of the flow at the outlet can be reduced as compared with the conventional one. Also, since the flow head curve goes down to the right even in the low flow area, even if pressure fluctuations occur due to cavitation, etc., the flow quantity does not easily fluctuate, so operation is stable and noise and vibration are suppressed. it can.
【図１】本発明による羽根車を示し、(A) は側板を省略
して示す正面図、(B) は縦断面図である。FIG. 1 shows an impeller according to the present invention, (A) is a front view showing a side plate omitted, and (B) is a longitudinal sectional view.
【図２】本発明の遠心ポンプの性能試験の結果を示す線
図である。FIG. 2 is a diagram showing the results of a performance test of the centrifugal pump of the present invention.
【図３】従来の遠心ポンプの羽根車を示し、(A) は側板
を省略して示す正面図、(B) は縦断面図である。FIG. 3 shows an impeller of a conventional centrifugal pump, (A) is a front view showing a side plate omitted, and (B) is a longitudinal sectional view.
【図４】従来の遠心ポンプの流量揚程特性を示す線図で
ある。FIG. 4 is a diagram showing a flow head characteristic of a conventional centrifugal pump.
10 羽根車 １ 主板 ２ 側板 ３ 羽根 ４ 羽根間流路 ５ ハブ ６ 腔所 ７ 入口 ８ 出口 10 Impeller 1 Main plate 2 Side plate 3 Blade 4 Flow path between blades 5 Hub 6 Cavity 7 Inlet 8 Outlet
Claims (2)
数の羽根によって複数の羽根間流路を限界してなる遠心
ポンプ又は圧縮機の羽根車において、上記羽根間流路の
入口から出口にかけて流過する流体の相対速度がほぼ一
定になるように上記羽根間流路の流路面積を形成したこ
とを特徴とする遠心式ポンプ又は圧縮機の羽根車。1. An impeller of a centrifugal pump or a compressor in which a plurality of vanes are bridged between a main plate and a side plate, and a plurality of vanes are bridged between the vanes. An impeller of a centrifugal pump or compressor, characterized in that the flow passage area of the inter-blade flow passage is formed so that the relative velocity of the fluid flowing through it is substantially constant.
から出口にかけて次第に厚くしたことを特徴とする請求
項１記載の遠心式ポンプ又は圧縮機の羽根車2. The impeller of a centrifugal pump or compressor according to claim 1, wherein the thickness of the vanes is gradually increased from the inlet to the outlet of the inter-blade passage.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24254095A JPH0968197A (en) | 1995-08-28 | 1995-08-28 | Impeller for centrifugal pump or compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP24254095A JPH0968197A (en) | 1995-08-28 | 1995-08-28 | Impeller for centrifugal pump or compressor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH0968197A true JPH0968197A (en) | 1997-03-11 |
Family
ID=17090635
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP24254095A Withdrawn JPH0968197A (en) | 1995-08-28 | 1995-08-28 | Impeller for centrifugal pump or compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0968197A (en) |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007082417A1 (en) * | 2006-01-21 | 2007-07-26 | Yangjiang City Xinli Industry Co., Ltd | Food centrifugal pump formed by pressing and welding |
| CZ300161B6 (en) * | 2006-12-01 | 2009-02-25 | Vysoké ucení technické v Brne | Impeller, particularly centrifugal pump impeller |
| CN101832292A (en) * | 2010-05-11 | 2010-09-15 | 浙江大学 | Paper pulp pump centrifugal open impeller based on fiber suspension flow design criteria |
| JP2011027070A (en) * | 2009-07-28 | 2011-02-10 | Panasonic Electric Works Co Ltd | Pump and fine bubble generator including the pump |
| CN102086885A (en) * | 2010-04-19 | 2011-06-08 | 江苏大学 | Five working condition point design method of impeller of non-overloading centrifugal pump |
| CN106050732A (en) * | 2016-08-16 | 2016-10-26 | 台州锦霸工贸有限公司 | Impeller assembly |
| CN106050733A (en) * | 2016-08-16 | 2016-10-26 | 台州锦霸工贸有限公司 | Impeller assembly in submersible pump for wells |
| CN106837814A (en) * | 2017-04-13 | 2017-06-13 | 海林金昌电机有限公司 | A kind of micro centrifugal pump |
| WO2018074591A1 (en) * | 2016-10-21 | 2018-04-26 | 三菱重工業株式会社 | Impeller and rotating machine |
| CN108317092A (en) * | 2018-02-02 | 2018-07-24 | 天津快透平科技发展有限公司 | Impeller and centrifugal compressor including the impeller |
| US11421702B2 (en) | 2019-08-21 | 2022-08-23 | Pratt & Whitney Canada Corp. | Impeller with chordwise vane thickness variation |
| CN118979895A (en) * | 2024-08-07 | 2024-11-19 | 清华大学 | A closed impeller and centrifugal compressor |
-
1995
- 1995-08-28 JP JP24254095A patent/JPH0968197A/en not_active Withdrawn
Cited By (16)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007082417A1 (en) * | 2006-01-21 | 2007-07-26 | Yangjiang City Xinli Industry Co., Ltd | Food centrifugal pump formed by pressing and welding |
| US8113802B2 (en) | 2006-01-21 | 2012-02-14 | Guangdong Winning Pumps Industrial Co., Ltd. | Food centrifugal pump formed by stamping and welding having a seal arrangement between the impeller and casing |
| CZ300161B6 (en) * | 2006-12-01 | 2009-02-25 | Vysoké ucení technické v Brne | Impeller, particularly centrifugal pump impeller |
| JP2011027070A (en) * | 2009-07-28 | 2011-02-10 | Panasonic Electric Works Co Ltd | Pump and fine bubble generator including the pump |
| CN102086885A (en) * | 2010-04-19 | 2011-06-08 | 江苏大学 | Five working condition point design method of impeller of non-overloading centrifugal pump |
| CN102086885B (en) * | 2010-04-19 | 2014-07-30 | 江苏大学 | Five working condition point design method of impeller of non-overloading centrifugal pump |
| CN101832292A (en) * | 2010-05-11 | 2010-09-15 | 浙江大学 | Paper pulp pump centrifugal open impeller based on fiber suspension flow design criteria |
| CN106050733A (en) * | 2016-08-16 | 2016-10-26 | 台州锦霸工贸有限公司 | Impeller assembly in submersible pump for wells |
| CN106050732A (en) * | 2016-08-16 | 2016-10-26 | 台州锦霸工贸有限公司 | Impeller assembly |
| WO2018074591A1 (en) * | 2016-10-21 | 2018-04-26 | 三菱重工業株式会社 | Impeller and rotating machine |
| US10859092B2 (en) | 2016-10-21 | 2020-12-08 | Mitsubishi Heavy Industries, Ltd. | Impeller and rotating machine |
| CN106837814A (en) * | 2017-04-13 | 2017-06-13 | 海林金昌电机有限公司 | A kind of micro centrifugal pump |
| CN108317092A (en) * | 2018-02-02 | 2018-07-24 | 天津快透平科技发展有限公司 | Impeller and centrifugal compressor including the impeller |
| CN108317092B (en) * | 2018-02-02 | 2024-07-23 | 天津快透平科技发展有限公司 | Impeller and centrifugal compressor comprising same |
| US11421702B2 (en) | 2019-08-21 | 2022-08-23 | Pratt & Whitney Canada Corp. | Impeller with chordwise vane thickness variation |
| CN118979895A (en) * | 2024-08-07 | 2024-11-19 | 清华大学 | A closed impeller and centrifugal compressor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Withdrawal of application because of no request for examination |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20021105 |